CN109328291A - Heat exchanger and the refrigerating plant for using it - Google Patents

Heat exchanger and the refrigerating plant for using it Download PDF

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Publication number
CN109328291A
CN109328291A CN201780038887.5A CN201780038887A CN109328291A CN 109328291 A CN109328291 A CN 109328291A CN 201780038887 A CN201780038887 A CN 201780038887A CN 109328291 A CN109328291 A CN 109328291A
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CN
China
Prior art keywords
plate fin
flow path
heat exchanger
protrusion
fluid
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Granted
Application number
CN201780038887.5A
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Chinese (zh)
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CN109328291B (en
Inventor
名越健二
山本宪昭
大城崇裕
奥村拓也
丸本彦
丸本一彦
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of CN109328291A publication Critical patent/CN109328291A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The present invention be have flowing the 1st fluid flow path plate fin laminated body each plate fin fold the 2nd fluid of interflow, between the 1st fluid and the 2nd fluid carry out heat exchange heat exchanger.In addition, being provided with multiple protrusions (22a, 22b) in the header areas or flow path u turn side end for being formed in the end of plate fin (2a).According to this structure, it can be improved the heat exchange contribution degree of the end of plate fin (2a), improve the heat exchanger effectiveness of plate fin (2a) entirety, small-sized and high performance heat exchanger is provided.

Description

Heat exchanger and the refrigerating plant for using it
Technical field
The present invention relates to heat exchanger and using its refrigerating plant, in particular to the plate wing of the plate of refrigerant will be flowed Piece is laminated and the heat exchanger of the plate fin laminated type of composition and the refrigerating plant using it.
Background technique
In general, being the refrigerating plant of representative by making by the system after compressor compresses using air conditioner and refrigeration machine Cryogen carry out heat exchange with room air with heat exchanger circulation that condenser and evaporator are representative carry out cooling supply or Person's heating.But the performance and energy saving as device are substantially controlled by the heat exchanger effectiveness of heat exchanger.Therefore, heat is handed over Parallel operation is strongly required high efficiency.
Among these, the fin-and-tube type that the heat exchanger of refrigerating plant is generally used for fins set perforation heat-transfer pipe and constitutes is warm Exchanger promotes the raising and miniaturization of heat exchanger effectiveness and realizing the downsizing of its heat-transfer pipe.
But there are limits for the downsizing of such heat-transfer pipe, therefore the raising and miniaturization of heat exchanger effectiveness are more next Closer to the limit.
On the other hand, in the heat exchanger for thermal energy, it is known to the structure by the power board fin stacking with flow path At plate fin laminated type heat exchanger.
The plate fin laminated type heat exchanger is in flowing in refrigerant i.e. the 1st fluid of the flow path formed among plate fin Heat exchange is carried out between the 2nd fluid between the plate fin being laminated with flowing, the quilt in for motor vehicle air conditioner etc. It is widely used (for example, referring to patent document 1).
Figure 31, Figure 32 indicate plate fin laminated type heat exchanger described in Patent Document 1, the heat exchanger 100 pass through by The plate fin 102 of flow path 101 with flowing refrigerant is laminated and constitutes plate fin laminated body 103.And it is laminated in plate fin The both sides laminated configuration of body 103 has end plate 104, is formed with 105 He of entrance side collector flow path in the left and right ends portion of flow path 101 Outlet-side header flow path 106 and constitute heat exchanger 100.
Existing technical literature
Patent document
Patent document 1: No. 3192719 bulletin of utility model registration
Summary of the invention
Plate fin laminated type heat exchanger described in Patent Document 1 passes through shape and 102 stamping concave groove of plate fin At flow path 101, therefore the sectional area of flow path 101 can be made smaller than heat-transfer pipe used in fin tube heat exchanger, Neng Gouti High heat exchanger effectiveness.
But the plate fin laminated type heat exchanger as recording in patent document 1 is deposited at the both ends of plate fin 102 In the low header areas for being known as entrance side collector flow path 105 and outlet-side header flow path 106 of heat exchange contribution degree, thus while Its heat exchanger effectiveness is improved compared with fin tube heat exchanger but there is also rooms for improvement.
In addition, flow path of the plate fin laminated type heat exchanger from entrance side collector flow path 105 to outlet-side header flow path 106 101 to be linear so short, as long as and because not making 102 length of plate fin that flow path dimensions cannot be made long, there is also heat to hand over The problem of parallel operation enlargement.
In such problems, the enlarged problem of the heat exchanger of the latter can be pressed down by making flow path 101U z bend The enlargement of making sheet fin 102 simultaneously ensures flow path length simultaneously, therefore can eliminate.
But even in this case, although the u turn side end of plate fin 102 and no entrance side collector stream Road 105, outlet-side header flow path 106 correspondingly reduce area, but the also portion low there are the heat exchange contribution degree of certain amplitude Point.
Wing plate 102 especially shown in figure sets up separately to be easy to carry out its stacking positioning during fabrication at both ends It is equipped with the pin hole of positioning pin, therefore the end of the plate fin 102 in flow path 101U z bend at least needs the area of pin hole, though It is not so width dimensions identical with the end of side for being provided with entrance side collector flow path 105 and outlet-side header flow path 106 But the also low part there are heat exchange contribution degree.
Moreover, because the downstream side portion of the pin hole of u turn side end be divided into dead water region thus pin hole downstream portion Dividing hardly has the function of heat exchange, and heat exchange contribution degree is extremely low.
The present invention provides the heat exchange contribution degree of end for improving plate fin, the heat exchanger of minitype high-performance and uses it Refrigerating plant.
The present invention is that the u turn side end of the header areas or flow path that are formed in the end of plate fin is provided with protrusion Structure.
Thereby, it is possible to improve the heat exchange contribution degree of the end of plate fin, the heat exchange effect of plate fin entirety can be improved Rate.And the downsizing of the flow path cross sectional area of the 1st fluid flowing path can be promoted on it, it is realized by the downsizing of flow path The raising of heat exchanger effectiveness.Therefore, it is capable of providing small-sized and high heat exchanger effectiveness heat exchanger.Moreover, by using in this way Heat exchanger, can be improved the heat exchange contribution degree of the end of plate fin, improve the heat exchanger effectiveness of plate fin entirety, can Small-sized and high heat exchanger effectiveness heat exchanger and the high-performance refrigerating plant high using its energy saving are provided.
Detailed description of the invention
Fig. 1 is the perspective view for indicating the appearance of heat exchanger of the 1st embodiment of the invention.
Fig. 2 is the exploded perspective view for indicating the heat exchanger of the 1st embodiment of the invention with the state separated up and down.
Fig. 3 is the exploded perspective view of the heat exchanger of the 1st embodiment of the invention.
Fig. 4 is the plate fin laminated arrangement for indicating the plate fin laminated body of heat exchanger of the 1st embodiment of the invention Side view.
Fig. 5 is the 5-5 sectional view of Fig. 1.
Fig. 6 is the 6-6 sectional view of Fig. 1.
Fig. 7 is the 7-7 sectional view of Fig. 2.
Fig. 8 is by coupling part and the collector of the inflow pipe and effuser of the heat exchanger of the 1st embodiment of the invention The perspective view that opening portion truncation indicates.
Fig. 9 is by the 1st fluid flowing path group part of the plate fin laminated body of the heat exchanger of the 1st embodiment of the invention The perspective view indicated is truncated.
Figure 10 is that the 1st fluid flowing path group part truncation of the heat exchanger of the 1st embodiment of the invention is indicated vertical Body figure.
Figure 11 is to cut the positioning pin bore portion of the plate fin laminated body of the heat exchanger of the 1st embodiment of the invention The disconnected perspective view indicated.
Figure 12 is that the collector opening portion of the plate fin laminated body of the heat exchanger of the 1st embodiment of the invention is truncated The perspective view of expression.
Figure 13 is the vertical view for constituting the plate fin of the plate fin laminated body of heat exchanger of the 1st embodiment of the invention Figure.
Figure 14 is to indicate that the amplification of the header areas of the plate fin of heat exchanger of the 1st embodiment of the invention is overlooked Figure.
Figure 15 is partially to indicate the structure amplification of the plate fin of the heat exchanger of the 1st embodiment of the invention Exploded perspective view.
Figure 16 A is the top view of the 1st plate fin of the heat exchanger of the 1st embodiment of the invention.
Figure 16 B is the top view of the 2nd plate fin of the heat exchanger of the 1st embodiment of the invention.
Figure 16 C is for illustrating the 1st plate fin and the 2nd plate fin of the heat exchanger of the 1st embodiment of the invention The plan view of the state of overlapping.
Figure 17 is acted for the refrigerant flowing of the plate fin for illustrating the heat exchanger of the 1st embodiment of the invention Figure.
Figure 18 is the protrusion for indicating to be arranged in the flow passage region of the plate fin of the heat exchanger of the 1st embodiment of the invention Amplification stereogram.
Figure 19 is to indicate to turn in the U-shaped of the 1st fluid flowing path of the plate fin of the heat exchanger of the 1st embodiment of the invention The amplification stereogram of the protrusion of curved side end setting.
Figure 20 be will as the heat exchanger of the 2nd embodiment of the invention plate fin laminated type heat exchanger with upper and lower The exploded perspective view that isolated state indicates.
Figure 21 is the vertical view for constituting the plate fin of the plate fin laminated body of heat exchanger of the 2nd embodiment of the invention Figure.
Figure 22 is partially to indicate the structure amplification of the plate fin of the heat exchanger of the 2nd embodiment of the invention Exploded perspective view.
Figure 23 is by the 1st fluid flowing path group portion of the plate fin laminated body of the heat exchanger of the 2nd embodiment of the invention The perspective view for dividing truncation to indicate.
Figure 24 be indicate the heat exchanger as the 3rd embodiment of the invention plate fin laminated type heat exchanger it is outer The perspective view of sight.
Figure 25 is to indicate that the heat exchanger from the 3rd embodiment of the invention removes the decomposition of the state after flow-dividing control pipe Perspective view.
Figure 26 is the flow-dividing control pipe insertion for indicating the plate fin laminated body of heat exchanger of the 3rd embodiment of the invention Partial perspective view.
Figure 27 is the perspective view of the flow-dividing control pipe of the heat exchanger of the 3rd embodiment of the invention.
Figure 28 is the sectional view for indicating the flow-dividing control tube portion of heat exchanger of the 3rd embodiment of the invention.
Figure 29 is the refrigeration using the conditioner of any heat exchanger of the 1st~the 3rd embodiment of the invention Circulation figure.
Figure 30 is the outline using the conditioner of any heat exchanger of the 1st~the 3rd embodiment of the invention Sectional view.
Figure 31 is the sectional view of existing plate fin laminated type heat exchanger.
Figure 32 is the top view of the plate fin of existing plate fin laminated type heat exchanger.
Specific embodiment
Hereinafter, the embodiments of the present invention will be described with reference to the drawings.
In addition, heat exchanger of the invention is not limited to the plate fin laminated type heat recorded in the following embodiments and the accompanying drawings friendship The structure of parallel operation further includes the structure for the heat exchanger being equal with the technical idea illustrated in the following embodiments.
In addition, embodiments described below it is merely meant that an example of the invention, indicated in embodiment structure, Function, movement etc. only illustrate, and non-limiting invention.
(the 1st embodiment)
Fig. 1 be indicate the heat exchanger as the 1st embodiment of the invention plate fin laminated type heat exchanger it is outer The perspective view of sight.Fig. 2 is the exploded perspective view for indicating the heat exchanger of present embodiment with the state separated up and down.Fig. 3 is The exploded perspective view of the heat exchanger of present embodiment.Fig. 4 is the plate fin layered laminate for indicating the heat exchanger of present embodiment The side view of state.In addition, Fig. 5~Fig. 8 is the sectional view of the heat exchanger of present embodiment respectively.
As shown in FIG. 1 to FIG. 8, the heat exchanger 1 of the heat exchanger as present embodiment has the system as the 1st fluid The entrance side collector flow path that cryogen flows into is the plate for flowing into pipe 4, multiple plate fin 2a of rectangular plate being laminated and are constituted Fin laminated body 2 and the outlet-side header that the refrigerant as the 1st fluid of the flow path in plate fin 2a is discharged Flow path, that is, effuser 5.
In addition, the two sides (being the upper side and lower side in Fig. 1) of the stacking direction in plate fin laminated body 2, are provided with vertical view It is end plate 3a, 3b of roughly the same shape with plate fin 2a.End plate 3a, 3b are formed by the plate with rigidity, such as pass through mill It cuts and intermetallic composite coating is carried out to aluminium, aluminium alloy, stainless steel and other metal materials and is formed.
In addition, end plate 3a, 3b, multiple plate fin 2a are brazed engagement with the state being laminated and are formed as one, it can also be with Joint element using other fixing means with heat resistance, for example chemical engages.
In addition, in the present embodiment, end plate 3a, 3b of the two sides of plate fin laminated body 2 are by screw bolt and nut or riveting The link mechanisms such as pin shaft 9, which link its length direction both ends, fixes.That is, end plate 3a, 3b of plate fin laminated body two sides are to press from both sides The form of plate fin laminated body 2 plate fin laminated body 2 is mechanically linked to fixation.
In addition, (being further left-hand end in Fig. 1 in the length direction one end of end plate 3a, 3b in the present embodiment Portion) header areas corresponding part be configured with reinforcing plate 16a, 16b, by by reinforcing plate 16a, 16b by link mechanism 9 It fastens and links and fix, end plate 3a, 3b are mechanically clamped plate fin laminated body 2 with being also included.
In addition, reinforcing plate 16a, 16b is also as end plate 3a, 3b by having the plate of rigidity, such as stainless steel, aluminium alloy Equal metal materials are formed, but it is preferred that reinforcing plate 16a, 16b and end plate 3a, 3b are comparably the higher material of rigidity or plate thickness more It is thick.
In addition, plate fin 2a has the 1st parallel fluid streams that flow the refrigerant as the 1st fluid, multiple internal Road group (the 1st fluid flow-path configuration of the plate fin 2a comprising the 1st fluid flowing path group is described in detail later), the 1st fluid flowing path Group is formed in substantially U-shaped, and the inflow pipe 4 that is attached thereto, effuser 5 are in the side of plate fin laminated body 2 (in Fig. 1 being Side) end plate 3a one end side i.e. the 1st end centralized configuration.
In the heat exchanger 1 of the present embodiment constituted in this way, composition plate is being formed in from the refrigerant that pipe 4 flows into is flowed into Multiple flow path groups of the inside of each plate fin 2a of fin laminated body 2, along its length parallel flowing, carry out u turn and It is discharged from inflection effuser 5.On the other hand, as the air of the 2nd fluid from the plate fin 2a's in composition plate fin laminated body 2 The gap formed between lamination passes through.The heat exchange of the refrigerant and the air as the 2nd fluid as the 1st fluid is carried out as a result,.
Then, use Fig. 9~Figure 19 to as the plate fin laminated body 2 of the main body of heat exchanger 1 and constitute the plate fin The plate fin 2a of laminated body 2 is illustrated.
Fig. 9 is to indicate the 1st fluid flowing path group part truncation of the plate fin laminated body of the heat exchanger of present embodiment Perspective view.The perspective view that 1st fluid flowing path group part of the heat exchanger of Figure 10 present embodiment indicates truncation.Figure 11 is The perspective view that the positioning pin bore portion truncation of the plate fin laminated body of the heat exchanger of present embodiment is indicated.Figure 12 be by The perspective view that the collector opening portion truncation of the plate fin laminated body of the heat exchanger of present embodiment indicates.Figure 13 is to constitute this The top view of the plate fin of the plate fin laminated body of the heat exchanger of embodiment.Figure 14 is the heat exchange for indicating present embodiment The enlarged plan view of the header areas of the plate fin of device.Figure 15 is to put the structure of the plate fin of the heat exchanger of present embodiment The exploded perspective view partially indicated greatly.Figure 16 A is the top view of the 1st plate fin of the heat exchanger of present embodiment.Figure 16B is the top view of the 2nd plate fin of the heat exchanger of present embodiment.Figure 16 C is for illustrating the heat of present embodiment The top view of 1st plate fin of the exchanger state Chong Die with the 2nd plate fin.Figure 17 is for illustrating that the heat of present embodiment is handed over The figure of the refrigerant flowing movement of the plate fin of parallel operation.Figure 18 is the plate fin for indicating to be arranged in the heat exchanger of present embodiment Flow passage region protrusion amplification stereogram.Figure 19 be indicate to be arranged in the heat exchanger of present embodiment plate fin The amplification stereogram of the protrusion of the u turn side end of 1 fluid flowing path.
As shown in figure 9, the 1st plate fin 2a of the heat exchanger of present embodiment different by stacking flow passage structure plate wings Piece 6 and the 2nd plate fin 7 and constitute.
As shown in figure 15, the 1st plate fin 6 of plate fin 2a by stamping by having in the 1st fluid stream being described in detail later 1st plate-shaped member 6a of line structure with and the identical 2nd plate-shaped member 6b of the 1st plate-shaped member structure soldered joint Face to face And it constitutes.Although it is not shown, still the 2nd plate fin 7 also with the 1st plate fin 6 likewise by by 2 plate-shaped members Face to face Soldered joint and constitute.In addition, the 1st plate-shaped member 6a, the 2nd plate-shaped member 6b are by the sheet metals structure such as aluminium, aluminium alloy, stainless steel At.
Hereinafter, being illustrated to the flow passage structure formed in plate fin 2a.
In addition, because plate fin 2a the 1st plate fin 6 and the 2nd plate fin 7 in addition to aftermentioned 1st fluid flowing path 11 Position is staggered identical with external structure, is illustrated so only illustrating 6 ground of the 1st plate fin in Figure 13~Figure 15.
As shown in the Figure 13 for indicating the 1st plate fin 6, plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7) is in length direction An end (in Figure 13 be left side) be formed with header areas H, other regions become flow passage region P.Moreover, in header region Domain H-shaped is connected at the collection tube opening 8b both sides of the collection tube opening 8a and outlet side that have entrance side and flows into pipe 4 and the (ginseng of effuser 5 According to Fig. 8).
In addition, being formed with multiple the 1st fluid flowing paths 11 as the 1st fluid flowing path, the 1st stream parallel in flow passage region P Refrigerant as 1st fluid of the body flow path from collection tube opening 8a, the 1st 11 groups of fluid flowing path is in plate fin 2a the (the 1st The 6, the 2nd plate fin 7 of plate fin) the other end (near the right-hand end of Figure 13) inflection, the collection tube opening 8b phase with outlet side Even.Specifically, 11 groups of the 1st fluid flowing path by the outlet side flow path portion 11a being connected of the collection tube opening 8a with entrance side and with go out The return road side flow path portion 11b that the collection tube opening 8b of mouth side is connected is constituted, u-shaped inflection.Moreover, the collector from entrance side is opened The refrigerant of mouthful 8a flows to the collection tube opening of outlet side from outlet side flow path portion 11a to the flow path portion 11b u turn of return road side 8b。
In addition, as amplification indicates in Figure 14, being formed with from collector around the collection tube opening 8a of entrance side The entrance side collector flow path 10 of 11 groups of the 1st fluid flowing path of refrigerant flow direction of opening 8a.The entrance side collector flow path 10 include with The peripheral flow path 10a that is formed from the mode of the periphery bulging of collection tube opening 8a, to the 1st fluid flowing path 11 of peripheral flow path 10a A connection flow path 10b that group side extends and by the connection flow path 10b and 11 groups of the 1st fluid flowing path of each 1st flow path, 11 phase Multiple-limb flow path 10c even.
In addition, the peripheral flow path 10a of entrance side collector flow path 10, connection flow path 10b are compared with multiple-limb flow path 10c and are being flowed Each 1st fluid flowing path 11 that road region P is set side by side is formed widerly, and the vertical sectional shape orthogonal with flow direction has square Shape shape.
In addition, the opening shape for integrating tube opening 8a of entrance side is greater than the opening shape of the collection tube opening 8b of outlet side as diameter Shape.This is because this is the case where heat exchanger is used as condenser, and in this case, the refrigeration after heat exchange The volume of agent becomes smaller.
In addition, with the number of the collection tube opening 8b of the outlet side return road side flow path portion 11b being connected than the collection from entrance side The number for the outlet side flow path portion 11a that the refrigerant of tube opening 8a flows into is set less.This is because with collection tube opening 8a, 8b Diameter it is different reason it is identical, the volume of the refrigerant after heat exchange becomes smaller.
In the present embodiment, the number for illustrating outlet side flow path portion 11a is 7, and the number of return road side flow path portion 11b is 2, but it's not limited to that.
In addition, in the case where the heat exchanger is used as evaporator, the entrance of refrigerant and the knot illustrated before Structure is opposite.
In addition, being opened at above-mentioned plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7) being formed with the collector from entrance side The region for the outlet side flow path portion 11a that the refrigerant of mouth 8a flows into and the return road side for being formed with the collection tube opening 8b for flowing to outlet side Between the region of flow path portion 11b, in order to which the mutual heat of the refrigerant in plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7) is passed It leads reduction (heat-insulated) and is formed with slit 15.
Moreover, entrance side collector flow path 10 connection flow path 10b outlet side flow path portion 11a, be biased to return road effluent The partly setting of road portion 11b opposite side.That is, as shown in figure 17, from through multiple-limb flow path 10c and outlet side flow path portion 11a phase The width V of flow path 11aa at end of the center line O of connection flow path 10b even to the return road side side flow path portion 11b is greater than from center line O To the width W with the flow path 11ab of return road side flow path portion 11b opposite side one end.Moreover, the connection flow path in the collection side tube opening 8a The end of 10b is formed with shunting impact walls 17 with the opening portion being connected outlet side flow path portion 11a, is located at connection flow path 10b Extended line on outlet side circuit portion become non-flow path portion 18.Therefore, the refrigerant from connection flow path 10b is touched with shunting It hits the collision of wall 17 and shunts (being to shunt in Figure 17 up and down), the multiple-limb flow path 10c flow direction for being connected the downstream side flow path 10b exists The upper and lower each 1st fluid flowing path group for the outlet side flow path portion 11a that non-flow path portion 18 is divided into.
In addition, the collection tube opening 8b in outlet side is also formed with outlet-side header flow path 14, the outlet-side header flow path 14 The essentially identical shape of entrance side collector flow path 10 in addition to not having to shunt impact walls 17, with the collection tube opening 8a that entrance side is arranged in Ground is formed.Moreover, in this embodiment, the number of the return road side flow path portion 11b of the 1st 11 groups of fluid flowing path is few to two, because This connection flow path 10b is arranged on the approximate centre line of return road side flow path portion 11b group.
At 2a (the 1st plate fin 6, the 2nd plate fin 7), in this example in the 1st plate fin 6, as shown in Figure 16 A like that, at it Flow passage region P (referring to Fig.1 3), in the longitudinal direction across specified interval be formed with multiple protrusions 12 (the 1st protrusion 12a, 12aa, 2nd protrusion 12b).
Figure 16 A is the top view of the 1st plate fin 6.Figure 16 B is the top view of the 2nd plate fin 7.Fig. 6 C is indicated the 1st plate The top view of the state Chong Die with the 2nd plate fin 7 of fin 6.
As shown in Figure 16 A~Figure 16 C, the 1st protrusion 12a, 12aa is in plate fin long side edge portion (in Figure 16 A, Figure 16 C For the long side edge portion of the left and right sides) flat end 19a and the flat end 19b of two sides edge of slit 15 be respectively formed. Moreover, as shown in Figure 10, the 1st protrusion 12a is connected to and the 1st plate fin 6 adjacent to and opposite the 2nd plate fin 7 in the stacking direction Long side edge portion flat end 19a, although it is not shown, the only plane of the two sides edge of the 1st protrusion 12aa and slit 15 End 19b is abutted, and distance between the stacking between the 1st plate fin 6 and the 2nd plate fin 7 is limited to defined length.Moreover, the 1st Protrusion 12a goes inwardly from the ora terminalis in each long side edge portion to be located at, for example removes 1mm or more (the 1st fluid inwardly from ora terminalis 11 side of flow path) the mode of position formed.
As shown in Figure 16 A, the 2nd protrusion 12b between 11 groups of the 1st fluid flowing path of flow path, in this case, it is become non-flow path The recession plane portion 20 in portion 18 is formed across specified interval.As shown in fig 16b, the 2nd protrusion 12b is connected to and the 1st plate fin 6 The recession plane portion 20 of the 2nd adjacent plate fin 7 in the stacking direction, by the 1st plate fin 6 and in the same manner as the 1st protrusion 12a Distance is limited to defined length between stacking between 2 plate fins 7.
In addition, as shown in figure 18, protrusion 12 (the 1st protrusion 12a, 12aa and the 2nd protrusion 12b) is by by the 1st plate fin 6 The a part in flat end 19a, 19b and recession plane portion 20 is cut forming and is formed.Protrusion 12 (the 1st protrusion 12a, 12aa, the 2 protrusion 12b) incision forming ora terminalis Y with plate fin 2a folded interflow the 2nd fluid the flowing side being depicted with arrows To opposite, forming standing piece Z is cut along the flow direction of the 2nd fluid.In the present embodiment, in the stream towards the 2nd fluid Cut forming with such section substantially U-shaped being open in dynamic direction.
Moreover, each protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) each plate fin 2a (the 1st plate fin 6, 2nd plate fin 7), the soldered joint of end plate 3 (3a, 3b) when make respective top surface be fixed in adjacent plate fin 2a (the 1st plate The 6, the 2nd plate fin 7 of fin), so that each plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7) integrally be linked.
In addition, the 1st protrusion 12a, 12aa and the 2nd protrusion 12b is to become straight line along the flow direction of the 2nd fluid (air) The mode of shape configures, and can also configure with being staggered.
In addition, as shown in figure 19, time of the plate fin 2a (6) in the flow passage region P of its 11 groups of u turn of the 1st fluid flowing path The fin planar portions 21 for rolling over the end of side are also formed with multiple protrusions 22 (the 3rd protrusion 22a, the 4th protrusion 22b).The protrusion 22 ( 3 protrusion 22a, the 4th protrusion 22b) it is formed also by fin planar portions 21 are cut forming.The protrusion 22 (the 3rd protrusion 22a, 4 protrusion 22b) incision forming ora terminalis Y and the 2nd fluid mobile phase pair.In addition, protrusion 22 (the 3rd protrusion 22a, the 4th protrusion The downstream side in positioning pin hole 13 22b) is set, and the 3rd nearest protrusion 22a of the downstream side in positioning pin hole 13 will be will position use Shape, such as the 2nd direction of fluid flow of direction of the fluid stream contraction in the downstream side of pin hole 13 are cut in the form of Ha font opening Forming.Moreover, each 4th protrusion 22b of further downstream is respectively under its center line and downstream side compared with the 3rd protrusion 22a The mode that the center line of one the 4th protrusion 22b is staggered is interconnected.
In addition, each protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b) also with protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd Protrusion 12b) equally, each top surface abutted with adjacent plate fin 2a (7) it is affixed, by between adjacent plate fin 2a gap limit It is set to fixed length and each plate fin 2a is connected to each other.
In addition, at plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7), as shown in Figure 11, H and stream in header areas The end of road region P is formed with the positioning pin hole 13 of the through hole as positioning.It is being laminated in plate fin 2a (the 1st plate wing The 6, the 2nd plate fin 7 of piece) two sides end plate 3a, 3b and reinforcing plate 16a, 16b be also formed with the positioning pin hole 13.Moreover, fixed Position with pin hole 13 can install be laminated multiple plate fin 2a (the 1st plate fin 6, the 2nd plate fins 7) when positioning pin fixture, with into The high-precision stacking of the other plate fin 2a of row, in this embodiment, using the reinforcing plate 16a of link plate fin laminated body 2, The link mechanisms such as the bolt of 16b and end plate 3a, 3b 9 (referring to Fig. 3) also serve as the mode of positioning pin fixture.
Peripheral part in the positioning pin hole 13 at the both ends for being set to plate fin 2a (the 1st plate fin 6, the 2nd plate fin 7) Point, it is formed with hole peripheral part (hereinafter referred to as positioning pin hole peripheral part) 13a of bulging up and down.The positioning pin hole peripheral part 13a is formed and is flowed the different space of the flow path of refrigerant, as shown in Figure 11, adjacent plate fin 2a in the stacking direction It is abutted between (6,7) (the 1st plate fin 6, the 2nd plate fin 7), becomes the header areas bearing in the stacking gap of holding plate fin 2a Portion.
Moreover, the positioning pin hole peripheral part 13a formed around the positioning pin hole 13 and the collection shown in Figure 13 Area under control domain H-shaped at entrance side collector flow path 10 and outlet-side header flow path 14 together, soldering be fixed in the stacking direction with Opposite other entrance side collector flow paths 10, outlet-side header flow path 14 and positioning pin hole peripheral part 13a, by plate fin 2a The end sections connection of (the 1st plate fin 6, the 2nd plate fin 7) is integral.
In addition, as the 1st fluid flowing path 11 of the invention, such as by the cross sectional shape orthogonal with the direction that refrigerant flows It is illustrated for circular shape, but further includes rectangular shape other than circular shape.
In addition, in the present embodiment, the 1st fluid flowing path 11 is pressed to carry out to the two side directions shape outstanding of stacking direction Illustrate, but can also be only protrudedly formed to the side of stacking direction.In addition, in the present invention, circular shape further includes circle Shape, ellipse and the compound curve shape formed by closed curve.
The heat exchanger of present embodiment is constituted as described above, is illustrated below to its function and effect.
Firstly, illustrating the flowing and heat exchange action of refrigerant.
Refrigerant from the inflow pipe 4 being connect with the one end side of plate fin laminated body 2 i.e. the 1st end, through the collection of entrance side Tube opening 8a is again through the peripheral flow path 10a around each plate fin 2a entrance side collector flow path 10 i.e. collection tube opening 8a, connection flow Road 10b, multiple-limb flow path 10c are to the 11 groups of flowings of the 1st fluid flowing path.It flow to 11 groups of the 1st fluid flowing path of each plate fin 2a Refrigerant is from its outlet side flow path portion 11a to the flow path portion 11b inflection of return road side, the collection through outlet-side header flow path 14, outlet side Refrigerant circuit flowing of the tube opening 8b from effuser 5 to refrigerating plant.
Moreover, refrigerant is folded with from the plate fin 2a of plate fin laminated body 2 when in the flowing of above-mentioned 1st fluid flowing path 11 The air that interlayer passes through carries out heat exchange.
Herein, because the heat exchanger of present embodiment is in the u turn side end of the 1st fluid flowing path 11 of plate fin 2a That is the 2nd end is provided with protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b), so can be improved without the 1st fluid flowing path 11 The heat exchange contribution degree of the u turn side end of plate fin 2a.Therefore, heat can be improved in the flow passage region overall length of plate fin 2a Exchange efficiency improves the thermal efficiency of heat exchanger.
Especially the u turn side end of plate fin 2a i.e. the 2nd end has positioning pin hole 13, and side becomes dead downstream Water area, therefore heat exchange contribution degree is extremely low, in the present embodiment, because being provided in the downstream side in positioning pin hole 13 more A protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b), so can be improved the heat exchange tribute of 13 downstream side universe of positioning pin hole Degree of offering.
Further, the 3rd nearest protrusion 22a of the downstream side in positioning pin hole 13, because using positioning pin hole 13 is shunk Downstream side fluid stream shape, so can make positioning pin hole 13 downstream side generate heat exchange contribution degree it is low Dead water region is minimum, can correspondingly further increase heat exchanger effectiveness.
Moreover, each protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b) is because it cuts the stream of forming ora terminalis Y and the 2nd Body stream is opposite, so leading edge effect can be generated in the part for cutting forming ora terminalis Y, can further increase heat exchanger effectiveness.
Moreover, be arranged in multiple protrusions 22 (the 3rd protrusion 22a, the 4th protrusion 22b) in the downstream side in positioning pin hole 13 at For being staggered relative to the 2nd fluid stream serpentine arrangement, therefore it all can effectively play heat exchange function, improve heat Exchange contribution degree.
Moreover, further, each protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b) is also fixed in adjacent plate with its top The short side part of plate fin 2a is linked with laminated arrangement and is fixed, therefore can be improved the rigid of plate fin laminated body 2 by fin 2a Property.
In addition, nearest the 3rd protrusion 22a in the downstream side that positioning pin hole 13 is arranged in is in towards the in the present embodiment The substantially U-shaped shape of section as the flow direction of 2 fluids is open cuts forming, it is however also possible to using as substantially The a pair of of L-shaped cuts the form for being shaped to opposite opposite, as long as becoming the stream for shrinking the downstream side in positioning pin hole 13 in fact The shape of body stream.
In addition, the heat exchanger of present embodiment is also equipped with multiple protrusions 12 in the flow passage region P of plate fin laminated body 2 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) improves the heat exchanger effectiveness of flow passage region P.Moreover, (the 1st protrusion of protrusion 12 12a, 12aa, the 2nd protrusion 12b) so that it cuts forming ora terminalis Y and protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b) equally In the flow direction of the 2nd fluid of the folded interflow of plate fin 2a, opposite mode is formed, and therefore, is made between plate fin lamination Interval is fixed, and makes the dead water region often generated in the downstream side of protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) It is minimum, and leading edge effect is generated cutting forming ora terminalis Y portion.Also, protrusion 12 is because with the flow direction phase with the 2nd fluid Pair mode cut forming, so the flow resistance relative to the 2nd fluid can also be made also small.It therefore, can be in suppressing plate wing The flow path resistance of the flow passage region P of laminate 2 greatly improves its heat exchanger effectiveness while increase.
In addition, the protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) of plate fin 2a is arranged in relative to the 2nd fluid Linearly assortment, if but the protrusion 12 be staggered or downwind side more formed than weather side etc. can more effective fruit, As long as selecting optimal structure according to the specification of heat exchanger, structure and the expectation of user.
In addition, because each protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) is between plate fin laminated body 2 The form of the flow direction opening of the air flowed in gap cuts forming, so not needing from the direction that air flows, i.e. with the 1st Recession plane portion 20 between 1st fluid flowing path in the direction that fluid flowing path intersects makes thinner thickness.Therefore, shape will be shaped by cutting At the 2nd protrusion 12b compared with cylindrical protrusion etc. swells the mode of formation like that so that between the 1st fluid flowing path Recession plane portion 20 can correspondingly narrow with the size for the thickness that do not need to make thinner, and can correspondingly make the width of plate fin 2a In other words degree minimizes heat exchanger.
Moreover, alternating dislocation configuration (reference of the ora terminalis of the long side part of plate fin 2a due to the 1st fluid flowing path 11 Narrow plane 20a and wide cut plane 20b Figure 10) are formed, forms protrusion 12a in the wide cut side plane 20b, top surface is fixed in phase The narrow plane 20a of adjacent plate fin 2a, therefore, it is not necessary to widen the width of the side narrow plane 20a to form protrusion. That is, by using wide cut plane 20b wide cut planar side be arranged cut forming protrusion abut with narrow plane 20a it is affixed, The width of the narrow planar side of plate fin long side part can not be widened and constant directly as narrow plane, it being capable of phase therewith Promote the miniaturization of heat exchanger with answering.
In addition, because protrusion 12 (the 1st protrusion 12a, 12aa, the 2nd protrusion 12b) is in each plate fin 2a, end plate 3a, 3b Each top surface is fixed in adjacent plate fin 2a when soldered joint, and each plate fin 2a is linked integral work so also having With can be improved the rigidity of plate fin laminated body 2.
Especially in the present embodiment, the extended line top of the connection flow path 10b of 11 groups of the 1st fluid flowing path is divided into non- A part, i.e. the 2nd protrusion of protrusion 12 (the 1st protrusion 12a, the 2nd protrusion 12b) is arranged using the non-flow path portion 18 for flow path portion 18 12b, therefore the plate fin stacking gap of 11 groups of parts of the 1st fluid flowing path can be securely maintained.Thus it enables that the 1st fluid stream The air-flow of the air of the 11 groups of parts in road is uniform and stable, to improve heat exchanger effectiveness.
In addition, the 1st protrusion 12a that the long side part of plate fin laminated body 2 is arranged in makes the plate wing for being easy to die down in intensity The intensity in the long side edge portion of laminate 2 improves, and is effective.It is more particularly set on the slit 15 of plate fin laminated body 2 1st protrusion 12a of both side edges part makes the intensity by the way that the slit edge point that slit 15 is broken, intensity declines is arranged It improves, therefore can also realize the deformation prevented near slit while the raising of heat exchanger effectiveness, be effective.In addition, 1st protrusion 12aa also can be set in the place for leaving slit 15.
In addition, the 1st protrusion 12a that the both side edges part of slit 15 is arranged in is arranged in a manner of across slit 15, at this In the case of kind, exists and heat biography occurs between 11 groups of the 1st fluid flowing path of outlet side flow path portion 11a and return road side flow path portion 11b It leads, the problem of the decline of the heat insulation of slit 15.But if as in the present embodiment in the both side edges part of slit 15 point It opens up and sets then such heat transfer disappearance, be effective.In addition, the 1st protrusion 12aa also can be set in the field for leaving slit 15 Institute.
In addition, the 1st protrusion 12a, 12aa of the long side part of plate fin laminated body 2 and the two side portions of slit 15 is arranged in It is located off the position of the ora terminalis of the plate fin long side of plate fin laminated body 2.Therefore, in the plate fin of plate fin laminated body 2 2a generates dew and stops water flow using the 1st protrusion 12a, 12aa when the dew flows discharge along the ora terminalis of plate fin 2a, It can prevent dew from accumulating in the part for being provided with the 1st protrusion 12a, 12aa, prevent various problems caused by dew in not So, it is capable of providing the heat exchanger of high reliablity.
As described above, the heat exchanger of present embodiment can be improved the heat exchange contribution degree of the end of plate fin, improve The heat exchanger effectiveness of heat exchanger entirety also has following such effect.
That is, being applied with refrigerant in the header areas H (referring to Fig.1 3) of plate fin laminated body 2 in this heat exchanger Strong pressure, with entrance side collector flow path 10 header areas H part etc. want dilatancy.
But it the header areas corresponding part of the plate fin laminated body 2 of heat exchanger shown in present embodiment, covers The header areas corresponding part of end plate 3a, 3b of the both sides of cover board fin laminated body 2 pass through link mechanism 9 for end plate 3a, 3b It is connected to each other.Therefore, the header areas corresponding part of end plate 3a, 3b dilatancy outward can be prevented.
That is, the high pressure for being applied to the refrigerant of entrance side collector flow path 10 will make the end plate 3a of top upward in Fig. 7 It deforms and deforms the end plate 3b of lower section downwards.But it is applied to the upward dilatancy power of the end plate 3a of top also By the downward pressure for flowing into refrigerant present in pipe 4 being connect from the end plate 3a with top, therefore with power counteracting Upward dilatancy power can prevent the dilatancy outward of the header areas corresponding part of the end plate 3a of top.And And be applied to lower section end plate 3b downward dilatancy power can by as already described by end plate 3b with it is upper The end plate 3a of side links to inhibit.As a result, dilatancy as a whole can be mitigated.
Especially in the present embodiment, the outer surface of the header areas corresponding part of end plate 3a, 3b is provided with enhancing Plate 16a, 16b, it is by link mechanism 9 (referring to Fig. 3) that reinforcing plate 16a, 16b is connected to each other, it is pressed from outside by end plate 3a, 3b To plate fin laminated body 2.Therefore, the intensity of the header areas corresponding part of end plate 3a, 3b is by reinforcing plate 16a, 16b self Rigidity is strengthened, and the dilatancy of its header areas corresponding part can be strongly inhibited.
In addition, also can by the flow passage structure that setting reinforcing plate 16a, 16b constitutes the U-shaped illustrated in present embodiment It is reliably suppressed the dilatancy of header areas corresponding part.That is, the plate fin laminated body 2 of present embodiment makes to be arranged in plate wing The u-shaped u turn of the 1st fluid flowing path 11 of piece 2a and entrance side collector flow path 10 and outlet-side header flow path 14 are concentrated on 1st end of the one end side as plate fin, therefore the dual-pressure in the part by entrance side and outlet side.But It, can even if applying such dual refrigerant pressure is also resistant against the pressure using structure shown in present embodiment Dilatancy is prevented by ground.
Therefore, for more than refrigeration dose as already described heat exchanger or compression ratio it is high environment it is corresponding In the case where the refrigerant of type, the dilatancy of the header areas part of plate fin laminated body 2 can be also prevented.Then, it ties Fruit is, such as is able to use the refrigerant of the high state of pressure as the corresponding refrigerant of the high environmental form of compression ratio, energy High-efficient heat exchanger is enough provided.
Moreover, in the heat exchanger, it can be by reducing the concave groove in plate fin 2a the 1st fluid flowing path formed Sectional area realize the downsizing of each flow path area of 11 groups of the 1st fluid flowing path (referring to Fig. 6), improve heat exchange effect Rate, and promote miniaturization.
That is, the dilatancy of the header areas corresponding part of plate fin laminated body 2 can be prevented, and at the same time realizing the 1st The downsizing of the flow path cross sectional area of fluid flowing path 11 is achieved in the promotion of raising and the miniaturization of heat exchanger effectiveness.
In addition, can will enhance due to setting because reinforcing plate 16a, 16b is only arranged in header areas corresponding part Plate 16a, 16b and increased volume increase is suppressed to minimum limit, can without detriment to heat exchanger miniaturization realize expansion The raising of deformation prevented with heat exchanger effectiveness.
In addition, in the header areas H (referring to Fig.1 3) of plate fin laminated body 2, because of the flow path of entrance side collector flow path 10 Area is maximum, so the refrigerant pressure of 10 part of entrance side collector flow path also highest.But because entrance side collector flow path 10 connect and are brazed with adjacent entrance side collector flow path 10, can be effectively prevented its dilatancy, can be more reliably Prevent the dilatancy of header areas corresponding part.
In addition, when the link mechanisms such as bolt 9 can be as plate fin 2a, end plate 3a, 3b, reinforcing plate 16a, 16b to be laminated Guidance pin (fixture) use, thereby, it is possible to improve stacking precision, and improve productivity.
In addition, though making header areas in the presence of the strong pressure of the refrigerant for the header areas H for being applied to plate fin laminated body 2 The problem of section deformation of the entrance side collector flow path 10 of H, but since the outer wall (flat surface) of entrance side collector flow path 10 is The state for abutting and being brazed in the stacking direction with adjacent other entrance side collector flow paths 10 in the stacking direction, thus it is each The pressure that refrigerant in a entrance side collector flow path 10 generates is cancelled, and can become will not deform and the knot of high reliablity Structure.
It is in substantially U in 11 groups of the 1st fluid flowing path of plate fin 2a setting in addition, in the heat exchanger of present embodiment Font is formed and inflection, therefore the 1st fluid flowing path length can not be made while plate fin 2a is increased and (lengthened length dimension) to become It is long.
Thereby, it is possible to improve the heat exchanger effectiveness of refrigerant and air, reliably make refrigerant become supercooling state and Improve the efficiency of refrigerating plant.It can also enough realizing the miniaturization of heat exchanger.
In addition, even if due to being shaped generally as U-shaped for 11 groups of the 1st fluid flowing path and by the entrance side collector stream of entrance side Road 10 and outlet-side header flow path 14 concentrate on one end side, thus the refrigerant pressure of the part of dual application header areas H, Also because as already described, the corresponding part of entrance side collector flow path 10 and outlet-side header flow path 14 by end plate 3a, 3b is connected to each other, but also further increases reinforcing plate 16a, 16b and prevent from deforming, so being reliably prevented from header areas H Corresponding part dilatancy.
In addition, in the present embodiment, the air for folding interflow with the plate fin in plate fin laminated body 2 carries out hot friendship The refrigerant changed flows to connection flow path 10b, multiple-limb flow path 10c, the 1st stream from entrance side collector flow path 10 as shown in Figure 14 11 groups of body flow path.Herein, impact walls 17, refrigerant and shunting are shunted because being provided in the downstream side of connection flow path 10b Impact walls 17 are collided to shunting up and down shown in Figure 14, are shunted from multiple-limb flow path 10c to each 1st fluid flowing path 11.By This, can prevent refrigerant from advancing with being extremely biased in the flow path of part on the extended line of connection flow path 10b.
In addition, as in the present embodiment by 11 groups of the 1st fluid flowing path u-shaped formation and when inflection, such as from Figure 17 As it will be appreciated that, each flow path length of the 1st 11 groups of fluid flowing path is more in periphery, in other words slit 15 far from U-shaped Flow path side it is longer, generate bias current caused by the difference of the flow path length.
But in the heat exchanger, as shown in Figure 17, make the connection flow path from entrance side collector flow path 10 Center line (not shown) deviation anti-return road flow path portion side of the 10b relative to 11 groups of the 1st fluid flowing path of outlet side flow path portion 11a Setting, therefore it is able to suppress bias current, so that each flow path is substantially evenly flowed refrigerant.
That is, in the heat exchanger, even if due to using the structure for making the 1st 11 groups of u turns of fluid flowing path, from the 1st stream The flow path length of the entrance side collector flow path 10 of 11 groups of body flow path of each flow path to outlet-side header flow path 14 is different and flow path Resistance changes, and the connection flow path 10b from entrance side collector flow path 10 also is located at counter the returning for being biased to outlet side flow path portion 11a The position of trackside flow path portion side.Therefore, it is more leaned on from the length on the shunting road of connection flow path 10b to each outlet side flow path portion 11a Nearly return road side flow path portion 11b is longer, thus the difference of offset resistance, it can be uniform to 11 groups of each flow path of the 1st fluid flowing path Ground shunts.
Therefore, it can promoted by 11 groups of the 1st fluid flowing path of u turnization and the synergistic effect of shunting homogenization Heat exchanger effectiveness higher heat exchanger 1 is obtained while miniaturization.
Moreover, because being formed between 11 groups of the 1st fluid flowing path of outlet side flow path portion 11a and return road side flow path portion 11b There is a slit 15 and completely cut off heat, so can prevent from 11 groups of the 1st fluid flowing path of outlet side flow path portion 11a to return road side flow path portion The heat of 11b is mobile, increases the heat exchange amount of refrigerant, realizes further increasing for heat exchanger effectiveness.
(the 2nd embodiment)
As shown in Figure 20~Figure 23, the shape of the 1st fluid flowing path group of the heat exchanger of the 2nd embodiment of the invention and The setting position for collecting tube opening is different from the heat exchanger of the 1st embodiment, to the heat exchanger phase having with the 1st embodiment The part of same function marks identical appended drawing reference, is illustrated centered on having the function of different parts.
Figure 20 is by the shape as the plate fin laminated type heat exchanger of the heat exchanger of present embodiment to separate up and down The exploded perspective view that state indicates.Figure 21 is the vertical view for constituting the plate fin of the plate fin laminated body of heat exchanger of present embodiment Figure.Figure 22 is the exploded perspective view for being indicated structure amplification a part of the plate fin of the heat exchanger of present embodiment. Figure 23 is the solid for indicating the 1st fluid flowing path group part truncation of the plate fin laminated body of the heat exchanger of present embodiment Figure.
In Figure 20~Figure 23,11 groups of the 1st fluid flowing path that plate fin 2a is arranged in of the heat exchanger of present embodiment is Linearly, it is provided with the collection tube opening 8a of entrance side in one end side i.e. the 1st end, the other end side is provided with outlet side Collection tube opening 8b.Pipe 4 is flowed into moreover, being connected in the collection tube opening 8a of entrance side, in the collection tube opening 8b connection of outlet side There is effuser 5, refrigerant linearly flow to the other end from the one end side of the plate fin 2a i.e. collection tube opening 8a of the 1st end The side i.e. collection tube opening 8b of the 2nd end and become linear outflow.
In addition, the entrance side collector flow path 10 formed around the collection tube opening 8a of entrance side includes the week of collection tube opening 8a Peripheral flow path 10a, connection the flow path 10b, multiple-limb flow path 10c enclosed.Connect flow path 10b with from peripheral flow path 10a along plate fin After the mode that the short side direction of 2a extends is formed, be connected with multiple-limb flow path 10c, outlet-side header flow path 14 also with the entrance The identical mode of side collector flow path 10 is constituted, and the two becomes symmetrical shape.
In addition, increasing shown in the Fig. 3 of end plate 3a, 3b of 2 two sides of plate fin laminated body without using the 1st embodiment of explanation Linked by link mechanism 9 to strong plate 16a, 16b, becomes the knot for preventing the dilatancy of header areas H at the both ends end plate 3a, 3b Structure.
The heat exchanger constituted like that above in addition to enabling 11 groups of the 1st fluid flowing path be formed as U-shaped and the effect that obtains, It is identical as the heat exchanger illustrated in the 1st embodiment including the structure of detail section, effect, thus omit the description.
In addition, the protrusion 22 (referring to Fig.1 3) the (the 3rd of the u turn side end setting in the plate fin 2a of the 1st embodiment Protrusion 22a, the 4th protrusion 22b) the header areas H of inlet porting side and the header areas H of outlet side are suitably set in this example ?.Namely based on be arranged in u turn side end protrusion 22 (the 3rd protrusion 22a, the 4th protrusion 22b) (referring to Fig.1 3 and figure 19) same thought, for example becoming the entrance side collector flow path 10 of dead water region, the downstream side shape of outlet-side header flow path 14 At equal.
(the 3rd embodiment)
The heat exchanger of 3rd embodiment of the invention is adapted as the entrance and exit phase of the refrigerant of heat exchanger The case where anti-evaporator uses is provided with point of refrigerant in outlet-side header flow path 14 such as Figure 24~as shown in Figure 28 Flow control tubulation 24.
In addition, feelings to use the heat exchanger of the structure of the 1st embodiment as evaporator in the present embodiment It is illustrated for condition.
Figure 24 is the solid for indicating the appearance of plate fin laminated type heat exchanger of the heat exchanger as present embodiment Figure.Figure 25 is the exploded perspective view for indicating the state after removing flow-dividing control pipe from the heat exchanger of present embodiment point.Figure 26 It is the perspective view for indicating the flow-dividing control pipe insertion portion of plate fin laminated body of the heat exchanger of present embodiment.Figure 27 is this The perspective view of the flow-dividing control pipe of the heat exchanger of embodiment.Figure 28 is the shunting control for indicating the heat exchanger of present embodiment The sectional view of tube portion.
In Figure 24~Figure 28, flow-dividing control pipe 24 is inserted into the collection for being set to the outlet side of the evaporation outlet as refrigerant Tube opening 8b, i.e. in outlet-side header flow path 14, front end as shown in figure 28, extends to the one of not set collection tube opening The end plate 3b of side becomes by the closed state of end plate 3b.Moreover, flow-dividing control pipe 24 is by compared with the internal diameter of collection tube opening 8b The pipe of path is constituted, and refrigerant circulation gap 25 is formed between collection tube opening inner surface, in its length direction, i.e. plate Multiple diffluence pass 26 are formed on the stacking direction of fin 2a at substantially equal intervals.
Multiple diffluence pass 26 are become with its aperture as the collection tube opening 8b in the direction flowed to refrigerant, i.e. outlet side is gone Small mode is formed.
In addition, flow-dividing control pipe 24 such as Figure 25, be mounted on reinforcing plate 16a as shown in Figure 27, by the way that reinforcing plate 16a is tight It is fixed in the end plate 3a of 2 two sides of plate fin laminated body and is inserted into setting in collection tube opening 8b.
In the reinforcing plate 16a for being equipped with above-mentioned flow-dividing control pipe 24, connect in another face opposite with flow-dividing control pipe 24 It connects to be fixed with and flows into pipe 4.
Effuser 5 is fixed in addition, being also connected in reinforcing plate 16a.In addition, flow-dividing control pipe 24, which can also use, closes it Front end, as the structure for abutting state with end plate 3b.
According to the heat exchanger constituted above, from the collection tube opening 8a as entrance side through 11 groups of the 1st fluid flowing path The refrigerant gas of outlet-side header flow path 14 is flow to as shown in the arrow of Figure 28, is existed from the refrigerant circulation warp of gap 25 Multiple diffluence pass 26 that the tube wall of flow-dividing control pipe 24 is formed are flowed into flow-dividing control pipe 24, from the collection tube opening 8b of outlet side Flow to effuser 5.
Herein, be arranged in the diffluence pass 26 of flow-dividing control pipe 24 with its aperture with being gone to the collection tube opening 8b of outlet side and The mode to become smaller is formed, therefore the refrigeration dose of each flow path at 11 groups of the 1st fluid flowing path can be made uniform.
That is, this heat exchanger by by the 1st fluid flowing path 11 downsizing and make the crushing of refrigerant compared to entrance Side collector flow path 10 is in the big several times of outlet-side header flow path 14.On the other hand, the distribution situation of the shunting of refrigerant by crushing Larger impact.As a result, in this heat exchanger, even if flow-dividing control pipe 24 is arranged in the prior art as the entrance of common sense Side collector flow path 10, the crushing of outlet-side header flow path 14 are also up to several times, therefore become the system flowed in the 1st fluid flowing path 11 Cryogen depends on the crushing of outlet-side header flow path 14, therefore cannot shunt as design.
But in the heat exchanger of present embodiment, the high outlet-side header of crushing is arranged in flow-dividing control pipe 24 Flow path 14, thus, it is possible to so as to the axis generated in big influence, up to several times outlet-side header flow path 14 is shunted The mode that the crushing in direction is evenly distributed is controlled.Thereby, it is possible to make in 11 groups of the 1st fluid flowing path of each flow path Refrigerant shunt volume is uniform.
In addition, the collection tube opening 8a for passing through entrance side from the refrigerant for flowing into the inflow of pipe 4 of this heat exchanger, is imported into 1st fluid flowing path 11 of the inside of each plate fin 2a flows into the collection tube opening 8b of outlet side, flows out from effuser 5.
At this point, due to the crushing generated in each flow path, the 1st fluid flowing path 11 of the plate fin 2a remote with from pipe 4 is flowed into (in Figure 28 for closer to the 1st fluid flowing path of the plate fin 2a on right side) is compared, from flowing into the of the close plate fin 2a of pipe 4 1 fluid flowing path 11 (being the 1st fluid flowing path closer to the plate fin 2a in left side in Figure 28) is easier flowing refrigerant.Change speech It, exists and generates a possibility that uneven in the flow of refrigerant.
Then, flow-dividing control pipe 24 is inserted into inside the collection tube opening 8b of outlet side, makes the shunting nearest from outlet side As shown in figure 28, make the outlet side that flow-dividing control pipe 24 is arranged in (is closer to a left side in Figure 28 to the opening area of mouth 26a The part of side) diffluence pass 26a with flow-dividing control pipe 24 anti-outlet side (in Figure 28 for closer to right side part) compared with More path, so that the crushing of the refrigerant passed through from diffluence pass be made to increase.Thereby, it is possible to not generate the bias current of refrigerant flow, Keep the refrigeration dose of the 1st fluid flowing path 11 of the inside of each plate fin 2a uniform, can be improved heat exchanger effectiveness.
As a result, the heat exchanger can be improved the heat exchanger effectiveness in the 1st 11 groups of parts of fluid flowing path, thermal effect is provided The higher heat exchanger of rate.
In addition, being only in flow-dividing control pipe using the homogenization structure that the refrigerant of flow-dividing control pipe 24 shunts further 24 punch the simple structure of diffluence pass 26, therefore can inexpensively provide.
Moreover, further, because flow-dividing control pipe 24 is integrally set to reinforcing plate 16a, can only pass through peace Dress reinforcing plate 16a, which is inserted into, to be set in outlet-side header flow path 14.Therefore, it can prevent from shunting by the additional installation such as welding The engagement of plate fin 2a caused by the brazing filler metal melts of the brazed portion of the inferior plate fin 2a of problems of the case where controlling pipe 24 The qualities such as the refrigerant leakage of bad and adjoint generation are bad, are capable of providing high-quality and efficient heat exchanger.
In addition, when reinforcing plate 16a connect and uses as evaporator with flow-dividing control pipe 24 and reinforcing plate 16a with outflow Potential difference between pipe 5 with flow-dividing control pipe 24 and effuser 5 are directly connected in the case where potential difference phase between the two It is formed than small material.Therefore, it can prevent from generating not in the case where flow-dividing control pipe 24 and effuser 5 to be directly connected to With the generation of metal contact corrosion, long term reliability can be greatly improved.Especially utilizing copper pipe to constitute inflow more Pipe 4, is constituted using stainless steel etc. in the air conditioner heat exchanger of flow-dividing control pipe 24 effuser 5, can be expected significant Effect, be effective.
In addition, reinforcing plate 16a is arranged in flow-dividing control pipe 24 in the present embodiment, but also can be set in end plate 3a Side, in addition, flow-dividing control can also be arranged in the opposite face of end plate 3a in the case where not using the type of reinforcing plate 16a Pipe 24 and effuser 5.
In addition, being envisioned for the shape of the 1st 11 groups of u turns of fluid flowing path in the present embodiment, but the 2nd is used to implement 11 groups linear of the 1st fluid flowing path illustrated in mode also can be applied similarly.
The heat exchanger illustrated in the structures of other detail sections, effect and the 1st embodiment is identical, to omit It is bright.
(the 4th embodiment)
4th embodiment of the invention is the system that one of heat exchanger of each embodiment shown in use before is constituted Device for cooling.
In the present embodiment, conditioner is illustrated as an example of refrigerating plant.Figure 29 is to make For the refrigeration cycle diagram of the conditioner of the refrigerating plant of present embodiment.Figure 30 is the refrigeration dress as present embodiment The summary sectional view for the conditioner set.
In Figure 29, Tu30Zhong, which is made of outdoor unit 51 and the indoor unit connecting with outdoor unit 51 52. The four-way valve of refrigerant circuit when outdoor unit 51 is configured with compressor 53, the switching cooling supply warming operation for compressing refrigerant 54, the pressure reducer 56 for exchanging the outdoor heat exchanger 55 of the heat of refrigerant and outside air and refrigerant being depressurized.In addition, Machine 52 indoors, the indoor heat exchanger 57 and indoor fan 58 of the heat configured with exchange refrigerant and room air.Moreover, logical It crosses refrigerant circuit compressor 53, four-way valve 54, indoor heat exchanger 57, pressure reducer 56 and outdoor heat exchanger 55 are connected And form heat pump type refrigerating circulation.
In the refrigerant circuit of present embodiment, use is basic ingredient with tetrafluoropropene or trifluoro propene, by difluoro first Alkane or pentafluoroethane or tetrafluoroethane so that global warming potential be 5 or more, 750 modes below, preferably 350 hereinafter, Further preferably 150 modes below mix the refrigerant that 2 kinds of ingredients or 3 kinds of ingredients are obtained by mixing respectively.
Four-way valve 54 is switched to the discharge of connection compressor 53 by conditioner shown in Figure 29 when for blowdown firing Side and outdoor heat exchanger 55.The refrigerant for becoming high temperature and pressure by the compressed refrigerant of compressor 53 as a result, passes through four-way Valve 54 is sent to outdoor heat exchanger 55.Then, refrigerant radiates with outside air with heat exchange is carried out, and becomes the liquid of high pressure Cryogen is sent to pressure reducer 56.It is depressurized and is become the two-phase system cryogen of low-temp low-pressure in pressure reducer 56, is sent to interior Machine 52.Machine 52 indoors, refrigerant enter the room heat exchanger 57, carry out heat exchange with room air and absorb heat, evaporation gasification And become the gas refrigerant of low temperature.At this time room air it is cooled and to indoor carry out cooling supply.Further, refrigerant returns to room Outer machine 51 returns to compressor 53 via four-way valve 54.
When carrying out warming operation, four-way valve 54 is switched to the discharge side and indoor unit 52 of connection compressor 53.As a result, The refrigerant for becoming high temperature and pressure by the compressed refrigerant of compressor 53, is sent to indoor unit 52 by four-way valve 54.High temperature The refrigerant of high pressure enters the room heat exchanger 57, carries out heat exchange with room air and radiates, and is cooled and becomes high pressure Liquid refrigerant.At this point, room air is heated, heat to interior.Later, refrigerant is sent to pressure reducer 56, is subtracting Depressor 56 is depressurized and becomes the two-phase system cryogen of low-temp low-pressure, is sent to outdoor heat exchanger 55, carries out heat with outside air It exchanges and evaporates gasification, return to compressor 53 via four-way valve 54.
The conditioner constituted in this way passes through real using the 1st in its outdoor heat exchanger 55 or indoor heat exchanger 57 Any heat exchanger in mode~the 3rd embodiment heat exchanger is applied, eliminates heat exchanger in the swollen of header areas part Bulging deformation, small-sized and high efficiency, therefore it is capable of providing the high high-performance refrigerating plant of energy saving.
As described above, the 1st invention is a kind of heat exchanger, in the heat exchange flow with the 1st fluid of flowing Each plate fin of the plate fin laminated body on road folds the 2nd fluid of interflow, carries out hot friendship between the 1st fluid and the 2nd fluid It changes.In addition, the plate fin of plate fin laminated body includes: flow passage region, there are multiple 1st fluids of the 1st fluid of parallel flowing Flow path；And header areas, there is the entrance side collector flow path and outlet side being connected to each 1st fluid flowing path of flow passage region Collector flow path, and the 1st fluid flowing path is formed and concave groove is arranged in plate fin.Moreover, in the header areas of plate fin It is provided with multiple protrusions.
According to this structure, the heat exchange contribution degree that can be improved the end of plate fin can be improved the heat of plate fin entirety Exchange efficiency.And the downsizing of the flow path cross sectional area of heat exchange flow path can be promoted on its basis, it is small by flow path The raising of boreization realization heat exchanger effectiveness.Therefore, it is capable of providing small-sized and high heat exchanger effectiveness heat exchanger.Moreover, logical It crosses using such heat exchanger, is capable of providing compact-sized and high energy saving high-performance refrigerating plant.
2nd invention is a kind of heat exchanger, in the plate fin laminated body with the heat exchange flow path for flowing the 1st fluid Each plate fin folds the 2nd fluid of interflow, carries out heat exchange between the 1st fluid and the 2nd fluid.In addition, plate fin is laminated The plate fin of body includes: flow passage region, has multiple 1st fluid flowing paths of the 1st fluid of parallel flowing；And header areas, With entrance side collector flow path and outlet-side header flow path that each 1st fluid flowing path with flow passage region is connected to, and the 1st flows Body flow path is formed and concave groove is arranged in plate fin.Moreover, making the 1st u-shaped U-shaped of fluid flowing path for being formed in plate fin It turns and will have the header areas of the entrance side collector flow path and outlet-side header flow path that are connected to the 1st fluid flowing path concentrate on 1st end of plate fin, and heat exchange is provided with protrusion in the 2nd end of the plate fin of u turn side with flow path.
According to this structure, plate fin can not be made long and keep the flow path dimensions of the 1st fluid flowing path long, to promote heat exchange The miniaturization of device and the raising of heat exchanger effectiveness, moreover, can by by the low entrance side collector flow path of heat exchange contribution degree and Heat exchanger effectiveness is improved in the one end side for being partially merely as plate fin i.e. the 1st end of outlet-side header flow path, further, energy The heat exchanger energy that the 2nd end of the plate fin of the side of the 1st fluid flowing path u turn is enough improved using protrusion, improves plate wing The heat exchanger effectiveness of piece entirety.Moreover, the downsizing of the flow path cross sectional area of the 1st fluid flowing path can be promoted on its basis, The raising of heat exchanger effectiveness is realized by flow path downsizing.Therefore, it is capable of providing small-sized and high heat exchanger effectiveness heat exchange Device.Moreover, being capable of providing compact-sized and high energy saving high-performance refrigerating plant by using such heat exchanger.
3rd invention is in the 1st or the 2nd invention, and protrusion is formed in a manner of cutting forming, and the incision of protrusion shapes ora terminalis It is made into the shape with the mobile phase pair of the 2nd fluid.
According to this structure, leading edge effect can be generated cutting forming end edge portion point, can correspondingly improves hot friendship Change efficiency.
4th invention be in the 1st~the 3rd invention, protrusion be formed in entrance side collector flow path, outlet-side header flow path or The downstream side of through hole is used in positioning, and is made into and is made entrance side collector flow path, outlet-side header flow path or positioning through hole The shape of the Flow Contraction stream in downstream side.
According to this structure, can make under entrance side collector flow path, outlet-side header flow path or positioning through hole The low dead water region of the heat exchange contribution degree that trip side generates is minimum, can correspondingly further increase heat exchanger effectiveness.
5th invention is in the 1st~the 4th invention, in the downstream side of protrusion with the flowing serpentine arrangement relative to the 2nd fluid Mode is provided with multiple protrusions formed in a manner of cutting forming.
According to this structure, not only have by entrance side collector flow path, outlet-side header flow path or positioning through hole The heat exchanger energy that the nearest protrusion in downstream side is realized, and have and the heat exchanger energy that forming protrusion is realized is cut by auxiliary, Heat exchanger effectiveness can be further increased.
6th invention is in the 1st~the 5th invention, and the top of protrusion is abutted with the surface of adjacent plate fin.
According to this structure, plate fin can be linked each other with layer-by-layer state by protrusion and is fixed, can be improved heat exchange Efficiency and the rigidity for improving plate fin laminated body.
7th invention is a kind of refrigerating plant, which uses the heat exchanger of any invention in the 1st~the 6th to make For the heat exchanger for constituting refrigeration cycle.
According to this structure, the heat exchanger of the refrigerating plant is small-sized and high efficiency, therefore can become the high height of energy saving Property refrigerating plant.
Industrial utilizability
The present invention can be improved the heat exchange contribution degree of the end of plate fin, improve the heat exchanger effectiveness of plate fin entirety, It is capable of providing small-sized and efficient heat exchanger and the high property refrigerating plant high using its energy saving.Thereby, it is possible to be in Front yard with and enterprise's air conditioner etc. used in widely utilize in heat exchanger and various refrigeration equipments etc., the value of industry It is very big.
Description of symbols
1,100 heat exchanger
2,103 plate fin laminated body
2a, 102 plate fins
3,3a, 3b, 104 end plates
4 flow into pipe
5 effusers
6 the 1st plate fins
The 1st plate-shaped member of 6a
The 2nd plate-shaped member of 6b
7 the 2nd plate fins
8,8a, 8b collection tube opening
9 link mechanisms (screw bolt and nut)
10,105 entrance side collector flow path (collector flow path)
10a peripheral flow path
10b connection flow path
10c multiple-limb flow path
11 the 1st fluid flowing paths
The outlet 11a side flow path portion
The return road 11b side flow path portion
12 protrusions
The 1st protrusion (protrusion) of 12a, 12aa
The 2nd protrusion (protrusion) of 12b
13 through holes (positioning pin hole (boss hole))
The hole 13a peripheral part (positioning pin hole peripheral part)
14,106 outlet-side header flow paths (collector flow path)
15 slits
16a, 16b reinforcing plate
17 shunt impact walls
18 non-flow path portions
19a, 19b flat end
20 recession plane portions
The narrow plane of 20a
20b wide cut plane
21 fin planar portions
22 protrusions
The 3rd protrusion (protrusion) of 22a
The 4th protrusion (protrusion) of 22b
24 flow-dividing control pipes
Gap is used in the circulation of 25 refrigerants
26,26a, 26b diffluence pass
27 hollow frames
51 outdoor units
52 indoor units
53 compressors
54 four-way valves
55 outdoor heat exchangers
56 pressure reducers
57 indoor heat exchangers
58 indoor fans.

Claims (11)

1. a kind of heat exchanger, in each plate fin of the plate fin laminated body of the heat exchange flow path with the 1st fluid of flowing Folded the 2nd fluid of interflow, carries out heat exchange, the feature of the heat exchanger between the 1st fluid and the 2nd fluid It is:
The plate fin of the plate fin laminated body includes: flow passage region, has and flows multiple the 1 of the 1st fluid parallel Fluid flowing path；And header areas, there is the entrance side collector being connected to each 1st fluid flowing path of the flow passage region Flow path and outlet-side header flow path, and the 1st fluid flowing path is formed and concave groove is arranged in the plate fin,
Moreover, being provided with multiple protrusions in the header areas of the plate fin.
2. a kind of heat exchanger, in each plate fin of the plate fin laminated body of the heat exchange flow path with the 1st fluid of flowing Folded the 2nd fluid of interflow, carries out heat exchange, the feature of the heat exchanger between the 1st fluid and the 2nd fluid It is:
The plate fin of the plate fin laminated body includes: flow passage region, has and flows multiple the 1 of the 1st fluid parallel Fluid flowing path；And header areas, there is the entrance side collector flow path being connected to each 1st fluid flowing path of the flow passage region With outlet-side header flow path, and the 1st fluid flowing path by the plate fin be arranged concave groove and formed,
Moreover, making the 1st u-shaped u turn of fluid flowing path for being formed in the plate fin and will have and connect with the 1st fluid flowing path The header areas of logical entrance side collector flow path and outlet-side header flow path concentrates on the 1st end of the plate fin, and described Heat exchange is provided with protrusion in the 2nd end of the plate fin of u turn side with flow path.
3. heat exchanger as described in claim 1, it is characterised in that:
The protrusion is formed in a manner of cutting forming, and the incision forming ora terminalis of the protrusion is made into the stream with the 2nd fluid Move opposite shape.
4. heat exchanger as claimed in claim 2, it is characterised in that:
The protrusion is formed in a manner of cutting forming, and the incision forming ora terminalis of the protrusion is made into the stream with the 2nd fluid Move opposite shape.
5. heat exchanger as described in claim 1, it is characterised in that:
The protrusion be formed in the entrance side collector flow path for being set to the plate fin, the outlet-side header flow path or The downstream side of through hole is used in positioning, and is made into and is made the entrance side collector flow path, the outlet-side header flow path or described fixed The shape of the Flow Contraction stream in the downstream side of position through hole.
6. heat exchanger as claimed in claim 2, it is characterised in that:
The protrusion be formed in the entrance side collector flow path for being set to the plate fin, the outlet-side header flow path or The downstream side of through hole is used in positioning, and is made into and is made the entrance side collector flow path, the outlet-side header flow path or described fixed The shape of the Flow Contraction stream in the downstream side of position through hole.
7. heat exchanger as described in claim 1, it is characterised in that:
It is also provided in a manner of relative to the flowing serpentine arrangement of the 2nd fluid in the downstream side of the protrusion multiple to cut It is split into the protrusion that the mode of shape is formed.
8. heat exchanger as claimed in claim 2, it is characterised in that:
It is also provided in a manner of relative to the flowing serpentine arrangement of the 2nd fluid in the downstream side of the protrusion multiple to cut It is split into the protrusion that the mode of shape is formed.
9. heat exchanger as described in claim 1, it is characterised in that:
The top of the protrusion is abutted with the surface of the adjacent plate fin.
10. heat exchanger as claimed in claim 2, it is characterised in that:
The top of the protrusion is abutted with the surface of the adjacent plate fin.
11. a kind of refrigerating plant, it is characterised in that:
The heat exchanger for constituting refrigeration cycle uses heat exchanger according to any one of claims 1 to 10.
CN201780038887.5A 2016-10-21 2017-10-13 Heat exchanger and refrigerating apparatus using the same Active CN109328291B (en)

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JP2016-206605 2016-10-21
JP2016206605A JP6906130B2 (en) 2016-10-21 2016-10-21 Heat exchanger and refrigeration system using it
PCT/JP2017/037132 WO2018074345A1 (en) 2016-10-21 2017-10-13 Heat exchanger and refrigeration device using same

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CN109328291A true CN109328291A (en) 2019-02-12
CN109328291B CN109328291B (en) 2020-07-17

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CN (1) CN109328291B (en)
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JP6906130B2 (en) 2021-07-21
WO2018074345A1 (en) 2018-04-26
CN109328291B (en) 2020-07-17
MY197027A (en) 2023-05-22

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